Machine for compression of fluids



A. c. LAYTON 2,646,207

MACHINE FOR COMPRESSION OF FLUIDS July 21, 1953 Filed July 3, 1951 2 Sheets-Sheet 1 INVENTOR Fl 6. l.

ARTHUR C. LAYTON ATTOR NEYS July 21, 1953 A. c. LAYTON MACHINE FOR COMPRESSION 0F FLUIDS 2 Sheets-Sheet 2 Filed July 3, 1951 a zoiuum M nd KU zoiuum INVENTOR ARTHUR CLAYToN m zoiuwm ATTORNEYS Patented July 21, 1953 MACHINE FOR'COMPRESVSIONOF FLUIDS Arthur Layton,. Tyler, Tex. I

7 Application July 3, 1951, Serial No. 235,040

rzcla ms. (or. 230-108)- condenser, receiver, and evaporator.

In the operation of a refrigeration system of this type, a quantityvof liquid refrigerant such as sulphurdioxide, methyl'chloride; or Freon is placed in'thereceiver. .The. refrigerant will then assume a pressure corresponding to its boiling point at the temperature of the receiverand environs. Liquidrefrigerant from the receiver, un-.

der pressure, is admittedto the evaporator where. it. is'vaporizedthrough absorption of heat from' the environs of the evaporator. The compressor "FUNVVIIJTED STATESFQATENT system-1s rendered-inoperative due to leaka e of the seal.

is used to remove from the evaporator this vaporized refrigerant. low pressure, is compressed to a' higher' pressure and, therefore assumes a higher temperature corresponding tothe new pressure conditions.

Heat of the vapor is removed in the condenser, where the cooled refrigerant reverts to the liquid state and flows intothe receiver to complete the cycle. From the above; it will be observed that r the function of the compressor is t o create an unbalancedpressure condition in the refrigeration system. Ideally, only gas vapor is handled by the compressor. However, oil from the coming pressures arefso high that motors. fail due The vapor, atrelativeiy Another important object is the reduction of wear to a minimum by elimination of unbalanced mechanical forces which are usually applied to moving parts.

Still another important object is the elimination of the necessity for high torque, slow speed motors. These are usually required dueto starting off under heavy load. Simple, high speed motors which are more economical in first cost former.

Apreferred form of the invention is shown on the attached drawings in which: n 'Y 1 Figure 1 shows a vertical section taken along the central axis of my machine;

Figure 2 is a horizontal cross-sectional view in which the upper right hand quadrant shows a section taken along the line AA in Figure 1; theupper left hand quadrant shows a section takenalong the line B--B of Figure 1; the lower left hand quadrant shows-a section taken along the line C"C Figure 1; andthe lower right hand quadrant shows a section taken along the line D-D, Figure 1;

and operating cost can be substituted for the Figure ,3 shows the vertical pipe assembly re-- i moved from the machine; and

to excessive head pressure. -Eliihination of this 7 difficulty isanotherob'ject cfth-isinvention.

Still another object 'is elimination of the compressorvalves' which are employed in conventionallcompressor's andwhich are rendered inopdue to ugs of oilforliquid refrigerant and by other mechanical, failures.

and moisture to the system. In either case the erative by minute particles of foreign substance holding the valvesopen, by breakage of the valves A ffurth'e r;. object is the lelimination of the 7 invention is the the body I I.

Figure 4 is a fragmentary vertical cross-secbase of the compressor.

7 The invention consists of a compressor body H, comprising upperpandlower halves, the two halves being fastened together to form a hermetically sealed vessel. Communicating pipes 12, herein referred to as the suction pipe, and 13, herein referred to as the discharge or hot. gas line are securedto the body ll, and connect to the evaporator and condenser respectivelyf The lower half of the body I I is formed with a pocket or sump I 4 disposed axially and projecting up? wardly from the lowest section of the interior of The sump 1| 4 has a plurality of radially disposed ports l5 communicating with the interiorof the body H v p 1 ,A vertical pipe I6 is disposed coaxially of the body H, communicates at its upper, end with the suction pipe I 2, and is connected at its lower end to the sump [4 by means of a central opening 31 in the top of the sump It. This pipe, i6 is formed 7 with apartition [1 located at its approximate mid-section which divides the pipe into an upper chamber I8 and lower chamber [-9. The upper endpof thepipe I 6 is securedby means of a locking nut 20 fitted into an annular recess near the top of the body II. The connection between the body H and the pipe !6 is hermetically sealed by means of the gasket 2i disposed axially between the nut 28 and the body H. The pipe 18 is formed with a horizontal exterior groove encircling it at the portion containing the partition ll, midway between the chambers l3 and 19, forming a space 23 around the circumference of the pipe [6. A plurality of radially disposed ports 22 lead from the extreme lower end of the chamber '18 to the space 23, and a corresponding group of radially disposed ports lead from the extreme upper section of the-chamber E9 to the space 23 and are designed to receive the noz z'les 24. n

A check valve 25, consisting of upper and lower 'guides and 58 respectively; and a movable disc 59 formed on a rod 66 inserted between the upper and lower guides and biased upwardly by a'spring 53 is located at the extreme upper end of the chamber [8 in an enlarged section of the pipe 6. The upper guide 5? of the check valve 25 forms locking means for securing the check valve in position. A gasket 25 between the upper guide and the shoulder formed in the pipe Hi hermetically seals the chamber !8 when the check valve is in the closed position.

An elongated sleeve 2! surrounds the upper section of the pipe 55, forms a bearing surface with it, and is free to rotate about it. Upward axial movement of the sleeve 2"! is prevented by a shoulder 28 formed in the upper section of the body I l. The lower end of the sleeve 2'? prcjects downwardly, incloscs a portion of the space 23 formed by the groove in the pipe l5, and carries a radially extended flange 25). This flange 29 is securely fastened to and supports a disc 33, which therefore rotates with the sleeve 27.

Another sleeve 3!, formed substantially the same as the sleeve 2'? exceptthat its flanged portion is located at its upper end, encircles the lower part of the pipe H5. The flanged end of the sleeve 3! extends upwardly to the space 23 and is securely fastened to'the disc 32, the sleeve and disc being free to rotate about the pipe [6. The discs 31) and 32 are disposed radially of the pipe 65 adjacent to the space 23, and are axially opposed. Axial movement downwardly of the sleeve 31 is prevented by the shoulder 3!! formed in the top of the sump Hi surrounding the central opening 37! which secures the pipe is. I

A plurality of curved elements 33 are regularly spaced between the discs 3!) and 32 said elements extending radially, and curving tangentially, to the periphery of the discs 38 and 532, the elements being secured between, and to, the discs by any convenient means, and forming therewith a plurality of elongated ports 34' constituting communieating means between the space 23 and the interior of the body l i. The assembly, consisting of the sleeves 27 and 3 i, the discs and 32, and the elements 33', is thus free to rotate as, a unit about the pipe E6, the pipe forming a bearing surface and supporting means for the assembly.

The armature, or rotor 35 of an electric motor, is formed as a ring secured to the sleeve 27 and disposed concentrically therewith and is located axially between the flange 29 and the shoulder 28, the rotor thus forming a part of the assembly as outlined above.

A tube 36 disposed axiallyof the chamber l8 projects downwardly through the port 33 formed in the partition I i and extends upwardly into the chamber l8 to a point just below the check valve, at which point the tube 36 makes a right angle turn and enters a port in the wall cf the pipe 16, thereby forming a communicating passage between the chamber i9 and a horizontal annular groove 5| in the exterior surface of the pipe. The connection between the tube 36 and the port 38, also the connection between the tube 35 and the port 59 are hermetically sealed from the charm ber I8.

Another port 39 in the wall of the pipe [5 is located at the lower end "of the pipe It just above the lower end of the sleeve 3 l This port leads to an annular groove 52 formed horizontally on the outer "surface of the pipe 16, and constitutes a communicating passage between the chamber 19 and the groove 52.

A diverter ring 4| carrying an outer flange 42 encircles the discs 30 and 32. Immediately therebelow a guide ring 44 in the shape of a centerless bowl carries a corresponding outer flange 45 which registers with flange 42 of the ring 4|. The body His forme'din upper and lower" halves and the interior sides of the mating edges of these halves are cut back to define a horizontal annular groove in which the flanges 42 and 4'5 are clamped between the upper and lower halves of the body H. Ports 33' in the flange 12 register with ports 45% in the flange 45 and constitute a passageway between the upper and lower halves of the chamber enclosed'by the body H.

A plurality of cylindrical perforated sleeves 43 of varying diameter, disposed axially and spaced radially, are suspended from the guide ring 4 3' and project downwardly to the bottom wall of the body H. The lower edges of the sleeves 48 are designed to permit liquid to flow along the bot tom wall of the body H to the ports 15in the sump i4. 7

An elongated sleeve 49' formed with a flared upper end encircles the sleeve 3! and the shoulder 40 of the sump IQ, the sleeve 49 being secured by any convenient means to the outer wall of the sump M above the ports [5. A port 4! is'fori'ned radially in the sleeve ail, the port 47 being located at any convenient point nearthe lower end of the sleeve 3!, and forming communicating means between the lower end of the space between the sleeves 3| and 49 and the interior of the body H.

A frusto conical dispersion plate 54 is a'fiix'e d to and supported by the mid's'ectior'i of the sleeve 49, the plate extending-radially therefrom and sloping downwardly to the inner cylindrical surface of the nearest perforated sleeve 48'.

A sleeve 55 containing the field or stator of an electric motor is afiixed to the interior of theu pper half of the body H and encircles the rotor 35 aflixed to the sleeve 21. I

A terminal plug 55 is located at any convenient point in the wall of the body If, and serves to form sealing and insulating means for inserting electric wires for connection; to the electric motor. The plug 56 is of standard manufacture and. is not claimed as a part of this" invention:

The various parts are rffably formed of metal suited to the design and application. While a particular preferred embodiment of the inven tion has been described, it will be apparent to those skilled in the art'that various changes and modifications maybe made without departing from the invention.

In operation (after first maxing suitable con-- nections with the evaporator, condenser and receiver, which complete a hermetically closed refrigeration system), the vapor compression. machine, hereinafter referred to as the coinpressor, is evacuated of all moisture and nonable for thepurpose.

;Befrigerant isnow added to the system inthe "desired quantity,. and pressures throughout the system reach a state of equilibrium in all parts offthe system, incuding the compressor. Liquid refrigerant is added at the receiverthe remaining partsof the system contain only refrigerant as before.

- vapor at the beginningthe -vapor condensing to a liquidunder suitable'temperature and pressure. conditions. The check valve 25 remains closed as long'as thepressure on the upper and lower side is balanced, the spring under the check valve forcing the check valve upwardly against the seat, the spring being just-strong enough to overcome the weight of the valve.

The motor is then. started by externalstarting means. The discs 30 and 32 bearing the curved elements 33 will assumethe speed of the rotor 35, as they are fixed to the sleeves?! and 31 .to form an assembly whichconstitutes the only rotating, or movable, partof this invention,-aside from the check valve. As heretofore pointed out the invention contemplates the use of high-speed ports- 34 is biased outwardly by centrifugalforce as the assembly is rotated, thi's iorce' being a function of the weight per .unit volume of the vapor, and the peripheral speed of the rotating discs 33and 32 Any vapor ejected from the ports 34 will cause. a reduction of pressure in the space 23 and consequently, inthechamber- 6 I ports 34- withthe vapor, are thrown tangentially againstthe sloping wall of the diverter ring 4! where the impact is small due to the angle of approach. The oil is thus spread thinly by the force of the impact and its velocity dissipated in aswirling motion about the wall of the guide ring 44. The oil then flows by gravitational effect down the sloping wall of the guide ring 44 and falls to the dispersion plate 54 and settles to the bottom wall of the body II to be re-cycled When the pressurein the system above the check valve exceeds the pressure. in the chamber [8, the spring pressure will be overcome'by the pressure difference and permit refrigerant vapor to flow into the-chamber l8, through the ports 22, into the space 23, and into the rotating ports 34 where it is ejected into the body H and out through the outlet. [3 to the condenser, (notshown). Additional vapor ejected into the body from the rotating ports 34 will produce a higher pressure in the body II and a greater'pressure differential between the body 'I l and the space 23. that the amount of oil delivered by thenozzles 24 be limited by the design of the nozzles 24 to obtain the desired operating pressure differential in the system. In the description'thus far the oil and refrigerant vapor have been considered as separate entities. Actually, the oil will absorb large quantities of refrigerant in either the vapor or liquid state. The amount of refrigerant absorbed by the oil will vary directly with the pressure and in versely as the temperature. Advantage is taken of this prBperty as follows: The oil contained in the body [I is under. relatively high pressure anclcontains a large amount of refrigerant.

' When refrigerant bearing oil is ejected from the lawith which that space communicates through the ports 22. -The' pressure in the chamber l9 will also be reduced by means of the nozzles 24. As rotation continues a constantly increas-- 7 ing pressure differential will be built :up between the vapor in the body H .and the vapor contained in the space 23, the; chamber l8, and

the .chamber {9. This pressure differential will cause'a downward pressure upon the. oil in the vlower portion of the body, ll, forcing the oil into the chamber 19 by means of the ports [5 and the sump I4. =This actionwill in turn produce arise injthe' oil level of the chamber [9 to'correspond with the pressure differential previously described. When the oil in the chamber Jlfihas completely filled the chamber, afurther' pressure. differential will causeoil to flow from the nozzles 24,;where it ispicked up by the rapidly rotating elements 33 "and directed into theports 34. Now, sincetheidensity of the oil is greater than the refrigerantvaporresiding in the ports the centrifugal effect on the oilfwill be "cor er, flow of oil fromthe .nozzles 24. From the- ,abovedescription .it will be observed that slugs of oil injected into the rotating ports 34 by the stationary nozzles 24 serve as movable pistons to ejectrefrigerant vapor from the ports 34 into nozzles, 24 it experiences 'a sudden reduction'of pressure, whereupon the refrigerant will expand and break; the oil up intoia foam, the foam oc-- I cupying a larger volume than the oil; consequently the rotating ports 34 will contain slugs of expanding foam which will'more effectively force the vapor ahead of the slugs of foam. Oil foam and vapor thrown tangentially against the diverter ring 4| will drive the vapor from the oil by the force of the impact. It is to be observed that the original quantity of vapor contained in the oil willbe re-absorbed since the pressure-- temperature conditions have been restored. Oil

and vapor'are directed through the perforated sleeves 48, the oil settling to the bottom off the vessel, while the vapor containing particles of oil pass through the remainder of the sleeves 48, the I oil particles being deposited on the sleeves 48 and settling to the bottom of the vessel, whilethe yapor continues upwardly throughthe ports 43 and 46 respectively, to the upper section of the ;body It and through the outlet l3 to the con- .denser (not shown). It is pointed out that oil is always present with the refrigerant in conventional refrigeration systems. While the oil has no refrigerating property'it acts as a very efiective retardant to'heat transfer in the evaporator and causes a loss in efficiency of the system. This ,defect is reduced or eliminated by my invention,

by removal of oil from the vapor while still in the compressor, as outlined above. While a pressure difference exists between the .lower end of the sleeve 3| and. the space 23, oil

, will leak into thespace forming the bearing surthe pressureyyessel comprising the interior of the body II. The slugs of oil ejected from the face between; the pipe [6 and the sleeve 3|. This l akaeaw ll;be e a iv mall and will s r to It i highly important form'a liquid seal to reduce leakage and will'also serve to lubricate the bearing between the pipe I6 and the sleeve BI, and the bearingbetween the sleeve 3| and the shoulder 40 which supports the rotating assembly. The grooves 52 and Si are provided externally of the pipe is to facilitate this lubrication. The groove 52 is supplied with oil under pressure by means of the port 39, while the groove 5| is supplied with oil under pressure by 'means of the port 38, the tube '36, and the port 'tlil. The sleeve 19 is provided to prevent oil from contacting the exterior of the sleeve 3|. It is pointed out that the sleeve at in rotating would cause a swirling of oil which could permit a complete loss of oil from the ports I5 and permit vapor to enter the chamber 19 from the ports 15. Contact'of oil with the exterior of the sleeve 3| would also produce a skin friction between the sleeve 31 and the oil. The small port 4"! formed in the wall of the'sleeve 58 serves t drain oil from the space about the sleeve 3 I.

One of the advantages of this invention over conventional compressors is due to the intimate relation between the vapor under compression in the ports 34 and the oil producing the compression. It is pointed out that in conventional compressors containing valves, the vapor must be compressed .to a higher pressure than exists in the system due to inertia of the valves which must be overcome before the compressed vapor loan be discharged into the system. After the valves are openedjby the pressure difference, a reexpansion takes place into the system which does no useful work. Also'to be observed is the fact that compression toahigher pressure thanexists in lthesysitem'will' produce a higher temperature the compressor. Both of these defects are reduced or eliminated in my invention. Another advantagejis du'ecto the heat absorbed by the oil during compression .and dissipated by the compressor .thus reducing some of the work of the condenser. 'Since ,theilower temperature of the oil'willefiect a-lowering of thecompression pressure and temperature, an increase in efliciency maybe jdbta'ined by coolingthe oil in-the compressor byiexternalmeans. This maybe effected by the simple method illustratedlin Figure 4 without ,depai ting'ffromthis invention. As shown in .this figure, th'eportsjib communicating with the sump TM are closed nit. .An auxiliary port'i'l is formed finthe sumpifito'serveas aninlet from the ex- ?terior the body I I Another port '62 in the bottom-Waller the'body i l adjacentto the sump ,li forms'anoutlet from the bottom of the body! i so that-oil' maybe directed through an auxiliary :circuit in the condenser by means of the second port andreturned to-the first port formed in the .sump. Pressure differential between the body 11 and-the chamber +9 will produce a circulation of'the oil-as beforeand effectan increase in the iefiiciencycf the-system. A further'increase of efficiency may-beeffected by proper design of the nozzles to -gi-ve-a maximum spouting velocity to-the oil. r I

'Thi's'invention may be-used-for a steam condenser eva-euation pump by substituting water 'i-or' the o'il; It-may also'be usedfor the compression of ai-r and-othergases by substituting a suitnble liquid. 1

What I claim-is? A fluid "oempr'esscr comprising a vertical cylindrical piessure vessel having separate upper and lower inner chambers formed coaXially-within said pressure-vesselso thatthebalance of the v-essel 'constitutes a-n; outer chamber encircling said inner chambers, an outlet from said outer chamber to and an inlet to said upper chamber from without the vessel, at least one communicating channel between the outer chamber and the lower end of said lower inner chamber, adjacent radial passageways from the upper end of said lower chamber and from the lower end of said upper chamber to said outer chamber, outwardly pointing nozzles in said first-named passageways, a sleeve rotatable about said inner chambers, said sleeve being divided into upper and lower sections, two axially opposed horizontal discs fixed to said sleeve between said sections, a plurality of arcuate spacers separating said discs and forming therewith a plurality of radial ducts in horizontal alignment with said radial passageways, said ducts curving continuously away from a line radial of said discs toward their perimeter, and means for rotating said sleeve about said chambers.

2. A compressor as claimed in claim 1 in which said inner chambers are formed by a cylindrical wall extending coaxially within said vessel and said wall serves as a bearing surface for said rotatable sleeve.

3. A compressor as claimed in claim 2 having cylindrical projections from the'upper and lower walls of said vessel which serve as bearing surfaces for said sleeve.

4. A compressor as claimed in claim 3 in which oil is carried in said lower inner chamber and the bearing surfaces formed for the rotating sleeve by the walls of the inner chamber are provided with special passages for the admission of oilpassing from said lower chamber to said bearing surfaces for-the lubrication thereof.

5. A compressor as claimed in claim 1 in which said vessel is formed of upper and lowersections secured together and has an interior annular groove where the sections meet, and in which a irusto-ccnical ring has a radially disposed outer flange clamped in said groove, said ring projecting inwardly above said ducts and said flange having a plurality of circumferentially spaced ports therein.

6. A compressor as claimed in'claim l in which said vessel is 'formed of upper and lower sections secured together and has an interior annular groove where the sections meet, and in which a. ringformed as a centerless bowl has an outer radial flange mounted in said groove, said flange having a plurality of circumferentially spaced ports and said ring projecting inwardly of said vessel, below said ducts.

7. A compressor as claimed-in claim 6 in which a frusto-conical ring carries an outer flange clamped into said groove, said frusto-conical ring extends inwardly of said vessel above said ducts and the flangesor" both of said rings carry regat its approximate mid-point a frusto-conical ring projecting outward and downward to the innermost of the perforated sleeves.

10. A compressor "asclaimed in claim 1 in which the channel between said outer chamber and the lower end of the inner chamber passes througha cooler.

11. A compressor as, claimed inclaim 1 in which a, pressure responsive valve at the entrance to said chamber controls the flow of fluid in the inlet to said upper chamber.

12. In combination, a compressor as claimed in claim 1 and an electric motor for rotating said compressor, said motor comprising a rotor fixed to the upper portion of said rotating sleeve and a stator fixed to the interior of the upper part of the outer wall of said outer chamber.

ARTHUR C. LAYTON.

Name Date Number Kittredge Sept, 15, 1914 Number Number Name Date: Skidmore, Jr Dec. 7, 1920 Marks Apr. 12, 1932 Bradley Mar. 31, 1936 Ford Jan. 28, 1941 Harrington May 18, 1943 Cushing July 4, 1950 FOREIGN PATENTS Country I Date France Dec. 22, 1928 

